US20040058772A1 - Toroidal-type continuously variable transmission and continuously variable transmission apparatus - Google Patents
Toroidal-type continuously variable transmission and continuously variable transmission apparatus Download PDFInfo
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- US20040058772A1 US20040058772A1 US10/644,770 US64477003A US2004058772A1 US 20040058772 A1 US20040058772 A1 US 20040058772A1 US 64477003 A US64477003 A US 64477003A US 2004058772 A1 US2004058772 A1 US 2004058772A1
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- axial
- continuously variable
- variable transmission
- toroidal
- rotary shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
- F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
- F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
- F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H37/086—CVT using two coaxial friction members cooperating with at least one intermediate friction member
Definitions
- the axial-direction two end portions of the output side disk 16 c are respectively rotatably supported by rolling bearings such as a pair of thrust angular ball bearings 42 , 42 .
- rolling bearings such as a pair of thrust angular ball bearings 42 , 42 .
- a pair of support posts 43 , 43 in the interior of a casing 11 through an actuator body 30 .
- the above-mentioned pair of support posts 43 , 43 are respectively connected and fixed to between the upper surface of the actuator body 30 and the lower surface of the connecting plate 48 in such a manner that the support posts 43 extend over and between the actuator body 30 upper surface and connecting plate 48 lower surface with the positions thereof restricted.
- the support post portions 44 a , 44 b which are disposed in the vicinity of the two end portions of the support posts 43 , 43
- the lower-side support post portions 44 a , 44 a are present at positions just above the upper surface of the actuator body 30 .
- support holes 51 b , 51 b which are formed in the lower-side support plate 25 b of the above-mentioned pair of support plates 25 a , 25 b , are fitted with the outer surfaces of the support post portions 44 a , 44 a of the two support posts 43 , 43 with no play between them. Also, the upper-side support post portions 44 b , 44 b are present at positions just below the lower surface of the connecting plate 48 .
- a first carrier 66 so as to extend between and over them, so that the input side disk 2 b and input rotary shaft 1 a can be rotated in synchronization with each other.
- two or more sets of planetary gears 75 , 76 which are respectively interposed between the second ring gear 74 and third sun gear 73 , are rotatably supported on the second carrier 72 .
- These planetary gears 75 , 76 are meshingly engaged with each other; and, the planetary gears 75 , which are disposed inside with respect to the diameter direction of the second carrier 72 , are meshingly engaged with the third sun gear 73 , while the planetary gears 76 disposed outside with respect to the diameter direction of the second carrier 72 are meshingly engaged with the second ring gear 74 .
Abstract
Description
- 1. Field of the Invention
- A toroidal-type continuously variable transmission and a continuously variable transmission apparatus according to the invention are used as an automatic transmission apparatus for a vehicle or a transmission apparatus for adjusting the operating speed of various industrial machines such as a pump.
- 2. Description of the Related Art
- As an example of a transmission which constitutes a transmission for a vehicle, there is known a toroidal-type continuously variable transmission; and, use of such toroidal-type of continuously variable transmission is enforced in part of the vehicle industry. The thus partly enforced toroidal-type continuously variable transmission is a toroidal-type continuously variable transmission of a so called double cavity type in which transmission of power from an input part to an output part is carried out using two systems disposed in parallel to each other. While a toroidal-type continuously variable transmission of this type is conventionally known because it is disclosed in a large number of publications such as U.S. Pat. No. 5,033,322, U.S. Pat. No. 5,569,112 and U.S. Pat. No. 5,651,750, description will be given below of the basic structure of toroidal-type continuously variable transmission of this type with reference to FIG. 7.
- A toroidal-type continuously variable transmission shown in FIG. 7 has an input rotary shaft1 which corresponds to a rotary shaft. On the peripheries of the near-to-middle-portion-base-end portion (in FIG. 7, the near-to-left-side portion) and the near-to-leading-end portion (in FIG. 7, the near-to-right-side portion) of the input rotary shaft 1, there are supported two
input side disks input side disks ball splines input side surfaces input side disks - Also, between the base end portion (in FIG. 7, the left end portion) of the input rotary shaft1 and the outer surface of the
input side disk 2 a, there are interposed a rollingbearing 5 and apressing device 6 of a loading cam type. And, acam plate 7, which constitutes thepressing device 6, is disposed in such a manner that it can be driven and rotated by adrive shaft 8. On the other hand, between the leading end portion (in FIG. 7, the right end portion) of the input rotary shaft 1 and the outer surface of the otherinput side disk 2 b, there are interposed aloading nut 9 and acountersunk plate spring 10 having large elasticity. - The middle portion of the input rotary shaft1 is inserted through a
penetration hole 13 which is formed in apartition wall portion 12 disposed within a casing 11 (see FIGS. 1 to 3, 5 which show the mode for carrying out the invention) in which the toroidal-type continuously variable transmission. A cylindrical-shaped output cylinder 28 is rotatably supported on the inside diameter side of thepenetration hole 13 by a pair ofrolling bearings output gear 15 is fixed to the outer peripheral surface of the middle portion of theoutput cylinder 28. Also, on such portions of the two end portions of theoutput cylinder 28 that respectively project from the two outer surfaces of thepartition wall portion 12, there are supported twooutput side disks output cylinder 28 - In this state, the
output side surfaces output side disks input side surfaces output side disks 16 a, 16 that project beyond the end edge of theoutput cylinder 28, there are interposedneedle roller bearings output side disks output side disks - Also, on each of such portions of the periphery of the input rotary shaft1 that are present between the input and
output side surfaces 3, 17 (cavities), there are disposed a plurality of (generally, two or three)power rollers power rollers peripheral surfaces output side surfaces power rollers trunnions displacement shafts needle roller bearings thrust ball bearings needle roller bearings displacement shafts displacement shafts trunnions - The
power rollers displacement shafts needle roller bearings thrust ball bearings power rollers needle roller bearings - Further, the
trunnions pivot shafts 32, 32 (see FIG. 3 which shows the mode for carrying out the invention), which are disposed on the two end portions (in the front and back direction in FIG. 7) of thetrunnions support plates casing 11, in such a manner that thepivot shafts trunnions pivot shafts actuators - When the above-structured toroidal-type continuously variable transmission is in operation, the
input side disk 2 a can be driven and rotated by thedrive shaft 8 through thepressing device 6. Since thepressing device 6 drives and rotates theinput side disk 2 a while generating an axial-direction thrust force, the pair ofinput side disks input side disk 2 a are respectively pushed toward their associatedoutput side disks input side disks power rollers output side disks output gear 15 which is connected to the respectiveoutput side disks output cylinder 28. - When the present toroidal-type continuously variable transmission is in operation, the surface pressures of the respective contact portions between the
peripheral surfaces power rollers output side surfaces pressing device 6. Also, these surface pressures increase as the power (torque) to be transmitted from thedrive shaft 8 to theoutput gear 15 increases. Therefore, there can be obtained good transmission efficiency regardless of variations in the torque. Also, even in case where the torque to be transmitted is 0 or quite small, the surface pressures of the contact portions can be secured to a certain degree by thecountersunk plate spring 10 and apre-load spring 26 which is disposed on the inside diameter side of thepressing device 6. Accordingly, the torque transmission in the contact portions can be carried out smoothly without incurring excessive slippage even immediately after start of the operation of the toroidal-type continuously variable transmission. - To change the transmission ratio between the
drive shaft 8 andoutput gear 15, thetrunnions actuators 31, 31 (see FIG. 3). In this case, thetrunnions trunnions peripheral surfaces power rollers output side surfaces trunnions pivot shafts trunnions 20. - Such swinging motion of the
trunnions 20 changes the positions of the contact portions between theperipheral surfaces power rollers output side surfaces side surfaces input side surface 3 and inwardly in the diameter direction of theoutput side surface 17 respectively, the more the transmission ratio changes to the speed increasing side. On the other hand, as shown in FIG. 7, the more the above contact portions changes inwardly in the diameter direction of theinput side surface 3 and outwardly in the diameter direction of theoutput side surface 17 respectively, the more the transmission ratio changes to the speed reducing side. - In the case of the conventional structure shown in FIG. 7, the
output cylinder 28 is rotatably supported on thepartition wall portion 12, the pair ofoutput side disks partition wall portion 12, and thepower rollers partition wall portion 12. This arrangement makes it troublesome to assemble thesupport plates trunnions casing 11. That is, to assemble the toroidal-type continuously variable transmission into thecasing 11, after thesupport plate 25 a situated on the deep side (in FIGS. 1 and 2, on the upper side) of thecasing 11 is assembled to thecasing 11 and theoutput cylinder 28 is assembled to thepartition wall portion 12, with the pair ofoutput side disks output cylinder 28, the input rotary shaft 1 must be inserted and further the fourtrunnions support plate 25 b on theactuator body 30 side (in FIGS. 1 and 2, on the lower side), theactuator body 30 and the pair ofinput side disks - The above assembling operation of the respective composing parts of the conventional structure must be carried out in a limited (small) space which is present within the
casing 11 and thus the assembling operation is troublesome. Also, in case where a poor operation is found in any one of the composing parts due to the errors of the dimensions of the parts and poor assembled conditions after they are assembled, it is also troublesome to cope with such poor operation. That is, in order to allow the toroidal-type continuously variable transmission to fulfill its expected performance, the position relationships between the composing parts must be restricted very strictly and, after assembled, it is necessary to make measurements as to whether the position relationships between the respective composing parts are accurate or not as well as whether the respective composing parts operate accurately or not. In case where this measuring operation finds any poor operation in the composing parts, the composing parts assembled must be dismantled and, as the need arises, the composing parts must be assembled again by changing the parts to be assembled (for example, by changing a shim for dimension adjustment). These dismantling and re-assembling operations must be respectively carried out in a limited space within thecasing 11, which is troublesome. Especially, in the case of a continuously variable transmission apparatus in which a toroidal-type continuously variable transmission and a planetary gear mechanism are combined together in order to increase the transmission ratio and enhance the durability and transmission efficiency, the number of parts to be assembled is large, which causes the above-mentioned problems to arise more often. - Further, in the case of the conventional structure shown in FIG. 7, since, between the
outer surfaces output side disks output gear 15 but also the pair ofrolling bearings partition wall portion 12 for supporting theserolling bearings outer surfaces output side disks - That is, in the speed reducing state of the toroidal-type continuously variable transmission shown in FIG. 7, the
peripheral surfaces power rollers output side surfaces output side disks peripheral surfaces output side surfaces output cylinder 28, are applied to theoutput side disks output side disks output side disks output side disks output side disks output side disks - On the other hand, in JP-2001-116097, there is disclosed a structure in which an output side disk of an integral type is rotatably supported on the periphery of the middle portion of an input side rotary shaft by a pair of radial needle roller bearings and a pair of thrust needle roller bearings. According to this structure, not only the
partition wall portion 12 can be omitted from the conventional structure shown in FIG. 7 but also dimension of the output side disk in a axial direction thereof can be shortened, therefore a toroidal-type continuously variable transmission can be reduced in size and weight as a whole. However, in the case of the structure disclosed in the above-cited publication JP-2001-116097, no consideration is given to the facilitation of an assembling operation. - The present invention aims at eliminating the drawbacks found in the above-mentioned conventional toroidal-type continuously variable transmission and continuously variable transmission apparatus. Accordingly, it is an object of the invention to provide a toroidal-type continuously variable transmission and a continuously variable transmission apparatus which not only can be reduced in size and weight but also can be assembled easily.
- In attaining the above object, according to one aspect of the invention, there is provided a toroidal-type continuously variable transmission, having: a casing; a rotary shaft rotatably supported in the interior of the casing; a pair of outside disks each including an axial-direction one-side surface having an arc-shaped section, the outside disks being respectively supported on the two end portions of the rotary shaft so as to be rotatable in synchronization with the rotary shaft in a state that axial-direction one-side surfaces opposed to each other; an inside disk including axial-direction two side surfaces each having an arc-shaped section, the inside disk being supported so as to be rotatable with respect to the rotary shaft in a state that the axial-direction two side surfaces respectively opposed to the axial-direction one-side surfaces of the two outside disks; support members interposed by two or more between the axial-direction two side surfaces of the inside disk and the axial-direction one-side surfaces of the two outside disks with respect to the axial direction of the toroidal-type continuously variable transmission so as to be swung and shifted about associated pivot shafts disposed at positions twisted with respect to the rotary shaft; a plurality of support plates for supporting the pivot shafts disposed on the two end portions of the support members; a plurality of power rollers each including a peripheral surface formed as a spherically projecting surface and respectively rotatably supported on the associated support plates, the peripheral surfaces of the power rollers being contacted with the axial-direction two side surfaces of the inside disk and the axial-direction one-side surfaces of the respective outside disks; an actuator of an oil pressure type for shifting the support members in the axial direction of associated pivot shafts; an actuator body storing the main body portion of the actuator therein; a pair of support posts including support ring portions, the support ring portions respectively existing in middle portions between the axial-direction two side surfaces of the inside disk and the axial-direction one-side surfaces of the two outside disks, wherein the respective one-side end portions of the two support posts are connected and fixed to the actuator body in a state that the rotary shaft is inserted through the support ring portions of the two support posts, the axial-direction two end portions of the inside disk are rotatably supported on the support ring portions of the two support posts, and the support plates are supported on the neighboring portions of the respective two end portions of the two support posts.
- According to the above construction, the present invention further includes a hollow rotary shaft disposed on the periphery of the middle portion of the rotary shaft so as to be rotatable with respect to the rotary shaft, wherein the inside disk is an integrally-formed output side disk, the base end portion of the hollow rotary shaft is connected to the output side disk so as to transmit the rotation power of the output side disk, the middle portion of the hollow rotary shaft is inserted through the inside diameter side of one of the two outside disks and the leading end portion of the hollow rotary shaft is projected from the axial-direction other end face of the present outside disk, thereby to take out the rotation power of the output side disk.
- According to the above construction, wherein the inside disk is an integrally-formed output side disk, an output gear is disposed on the outer peripheral edge of the output side disk, and the rotation power of the output side disk is taken out by the output gear.
- According to the above construction, wherein the rotary shaft, the pair of outside disks, the inside disk, the plurality of support members, the plurality of support plates, the plurality of power rollers, the plurality of actuators, and the pair of support posts are assembled to the actuator body before being stored into the casing.
- According to the above construction, wherein, in the portion of the casing that is situated on the lower side when the casing is carried on a vehicle, there is formed the opening; and, an actuator body including the rotary shaft, the pair of outside disks, the inside disk, the plurality of support members, the plurality of support plates, the plurality of power rollers, the plurality of actuators, and the pair of support posts is stored into the casing through the opening, and the actuator body is connected and fixed to the casing.
- According to the above construction, the present invention is a half-toroidal-type continuously variable transmission in which lines connecting the center axes of the pivot shafts serving as the inclination centers of the power rollers to the rolling contact positions between the peripheral surfaces of the power rollers and the axial-direction side surfaces of the outside and inside disks are free from presenting on the same straight line.
- According to the above construction, wherein the support members and the power rollers are interposed between the axial-direction one-side surfaces of the pair of outside disks and the axial-direction two-side side surfaces of the inside disk by two at two positions on the opposite side in the diameter direction of the respective disks
- Another aspect of the invention is a continuously variable transmission apparatus, in combination a toroidal-type continuously variable transmission unit with a planetary-gear-type transmission unit, having: an input shaft connected to the rotary shaft of the toroidal-type continuously variable transmission unit; and an output shaft connected to the composing parts of the planetary-gear-type transmission unit, wherein the toroidal-type continuously variable transmission unit, has: a casing; a rotary shaft rotatably supported in the interior of the casing; a pair of outside disks each including an axial-direction one-side surface having an arc-shaped section, the outside disks being respectively supported on the two end portions of the rotary shaft so as to be rotatable in synchronization with the rotary shaft in a state that axial-direction one-side surfaces opposed to each other; an inside disk formed as an integral body or including a pair of elements connected together and including axial-direction two side surfaces each having an arc-shaped section, the inside disk being supported so as to be rotatable with respect to the rotary shaft in a state that the axial-direction two side surfaces respectively opposed to the axial-direction one-side surfaces of the respective outside disks; support members interposed by two or more between the axial-direction two side surfaces of the inside disk and the axial-direction one-side surfaces of the respective outside disks with respect to the axial direction of the toroidal-type continuously variable transmission so as to be swung and shifted about associated pivot shafts thereof disposed at positions twisted with respect to the rotary shaft; a plurality of support plates for supporting the pivot shafts disposed on the two end portions of the support members; a plurality of power rollers each including a peripheral surface formed as a spherically projecting surface and respectively rotatably supported on the associated support plates, the peripheral surfaces of the power rollers being contacted with the axial-direction two side surfaces of the inside disk and the axial-direction one-side surfaces of the two outside disks; an actuator of an oil pressure type for shifting the support members in the axial direction of the associated pivot shafts; an actuator body storing the main body portion of the actuator therein; a pair of support posts each including a support ring portion, the support ring portions respectively existing in the middle portion between the axial-direction two side surfaces of the inside disk and the axial-direction one-side surfaces of the two outside disks, wherein the respective one-side end portions of the two support posts are connected and fixed to the actuator body in a state that the rotary shaft is inserted through the support ring portions of the two support posts, the axial-direction two end portions of the inside disk are rotatably supported on the support ring portions of the two support posts, and the support plates are supported on the neighboring portions of the two end portions of the two support posts, the planetary-gear-type transmission unit is structured such that the power is transmitted thereto from the rotary shaft and the inside disk of the toroidal-type continuously variable transmission unit, the planetary-gear-type transmission unit includes a switching device for switching the transmission passage of the power into two systems.
- According to the above construction, the present invention further including: a hollow rotary shaft disposed on the periphery of the middle portion of the rotary shaft, and wherein the planetary-gear-type transmission unit further has: a carrier connected and fixed to the pair of outside disks including the toroidal-type continuously variable transmission unit concentrically with the two outside disks and rotating with the both of outside disks; a plurality of first planetary gears rotatably supported on one of the axial-direction two side surfaces of the carrier opposed to one of the outside disks; a first sun gear connected to the inside disk by the hollow rotary shaft not only disposed concentrically with the inside and outside disks so as to be rotatable but also meshingly engaged with the first planetary gears; a plurality of second planetary gears rotatably supported on the other side surface of the carrier; a second sun gear not only disposed concentrically with the inside and outside disks so as to be rotatable but also meshingly engaged with the second planetary gears; and, a ring gear not only disposed concentrically with the input side and output side disks so as to be rotatable but also meshingly engaged with the first planetary gears, wherein the switching device selects a mode for transmitting the power taken out from the inside disk through the ring gear to the output shaft or a mode for transmitting the power taken out from the inside disk through the second sun gear to the output shaft.
- As described above, in the case of a toroidal-type continuously variable transmission and a continuously variable transmission apparatus according to the invention, not only the inside disks but also the plurality of support members and power rollers can be supported at their respective given positions by the pair of support posts with their respective one-end portions connected and fixed to the actuator body. Therefore, the main portions of the toroidal-type continuously variable transmission can be assembled outside the casing before the toroidal-type continuously variable transmission is assembled into the casing. Accordingly, the assembling operation can be executed in a wide space, thereby being able to facilitate the assembling operation. Also, after assembly of the main portions of the toroidal-type continuously variable transmission, before the toroidal-type continuously variable transmission is stored into the casing, the operating states of the present main portions can be confirmed. And, in case where the operating state are found poor, dismantling and re-assembly of the main portions can be carried out easily in a wide space outside the casing. Also, it is easy to repair the main portions when a trouble occurs.
- Also, in the case of a toroidal-type continuously variable transmission and a continuously variable transmission apparatus according to the invention, since the inside disks are rotatably supported by the pair of support posts, differently from the previously-described conventional structure, there is eliminated the need to interpose the rolling bearings and the partition wall portion for supporting the rolling bearings between the pair of inside disks. Therefore, the distance between the two inside disks can be shortened and the two inside disks can be formed as an integral body, which makes it possible to reduce the toroidal-type continuously variable transmission in size and weight.
- FIG. 1 is a section view of an embodiment of the mode for carrying out the invention;
- FIG. 2A is an enlarged view of the A portion shown in FIG. 1;
- FIG. 2B is an enlarged view of the A portion shown in FIG. 1 which shows an embodiment outputting the power from the output side disk;
- FIG. 3 is a section view taken along the line B-B shown in FIG. 1;
- FIG. 4 is a perspective view of a module serving as the main portions of a continuously variable transmission apparatus, showing a state before it is stored into a casing;
- FIG. 5 is a perspective view of a casing, showing a state in which the casing is viewed from bottom;
- FIG. 6 is a graphical representation of the relationship between the transmission ratio of a toroidal-type continuously variable transmission and the transmission ratio of the whole of a continuously variable transmission apparatus in a state where the rotation speed of an engine is kept constant; and,
- FIG. 7 is a section view of an example of the basic structure of a conventionally known toroidal-type continuously variable transmission.
- Now, FIGS.1 to 5 show an embodiment of the mode for carrying out the invention. By the way, FIGS. 1 to 3 show the dimensional relationship of the embodiment such as the aspect ratio thereof using the actual dimensional relationship thereof. Also, in FIGS. 4 and 5 which are respectively perspective views of the embodiment as well, this dimensional relationship is drawn substantially in accordance with the actual dimensional relationship. A continuously variable transmission apparatus according to the present embodiment is composed of a combination of a toroidal-type continuously
variable transmission unit 33 corresponding to a toroidal-type continuously variable transmission and first to third planetary-gear-type transmission units 34 to 36, and further includes an inputrotary shaft 1 a corresponding to a rotary shaft and anoutput shaft 37. In the illustrated embodiment, between the inputrotary shaft 1 a andoutput shaft 37, there is interposed atransmission shaft 38 in such a manner that it is concentric with the twoshafts shafts type transmission units rotary shaft 1 a andtransmission shaft 38, while the third planetary-gear-type transmission unit 36 is disposed in such a manner that it is set over and between thetransmission shaft 38 andoutput shaft 37. - Of the above transmission units, the toroidal-type continuously
variable transmission unit 33 includes a pair ofinput side disks output side disk 16c, and a plurality ofpower rollers input side disks rotary shaft 1 a in such a manner that they are concentric with each other and can be rotated in synchronization with each other. Also, theoutput side disk 16 c is supported between the twoinput side disks input side disks input side disks power rollers more power rollers 19 are held respectively by and between the axial-direction two side surfaces of theoutput side disk 16 c and the axial-direction one-side surfaces of the twoinput side disks power rollers input side disks power rollers 19 transmit the power from the twoinput side disks output side disk 16 c. - FIG. 2B shows an embodiment outputting the power from the
output side disk 16 c. Anoutput gear 16 d is disposed on the outer peripheral edge of theoutput side disk 16 c, and the rotation power of theoutput side disk 16 c is taken out by theoutput gear 16 d. - Also, in the present embodiment, as shown in FIG. 3, a pair of
bent wall portions trunnions power rollers bent wall portions members members 40 are respectively disposed so as to step over their associatedpower rollers 19 and, at the same time, in a state where the two end faces of the connectingmembers 40 are butted against the mutually opposing inner surfaces of thebent wall portions trunnion members 40 are respectively connected and fixed to their associatedtrunnions screws members respective trunnions trunnions displacement shafts 21 a from being inclined due to thedeformed trunnions power rollers displacement shafts 21 a, thereby being able to stabilize the transmission operation of the continuously variable transmission apparatus. By the way, in the case of the present embodiment, each of thedisplacement shafts 21 a and an outer race constituting athrust ball bearing 23 supporting thepower roller 19 in a rotatable manner are formed as an integral body. - Further, in the case of the present embodiment, the axial-direction two end portions of the
output side disk 16 c are respectively rotatably supported by rolling bearings such as a pair of thrustangular ball bearings support plates trunnions casing 11 through anactuator body 30. The support posts 43, 43 are formed in such a manner that a pair ofsupport post portions rotary shaft 1 a between them so as to be concentric with each other, are connected together by a circular-ring-shapedsupport ring portion 45. The inputrotary shaft 1 a penetrates through the inside portion of thesupport ring portion 45. - Also, the lower end portions of the respective support posts43, 43 are respectively connected and fixed to the upper surface of the
actuator body 30 by a plurality ofbolts actuator body 30, there are formed recessedportions portions portions actuator body 30 from bottom and are threadedly engaged with the screw holes; and further, the support posts 43, 43 are fixed at given positions in the upper surface of theactuator body 30 using the tightly fastenedbolts - On the other hand, the upper end portions of the support posts43, 43 are respectively connected and fixed to the lower surface of a connecting
plate 48 by their associatedbolts plate 48, there are formed recessedportions portions plate 48 from above and are threadedly engaged into their associated screw holes; and further, the support posts 43 are fixed at their respective given positions in the lower surface of the connectingplate 48 by their associatedbolts - The above-mentioned pair of support posts43, 43, as described above, are respectively connected and fixed to between the upper surface of the
actuator body 30 and the lower surface of the connectingplate 48 in such a manner that the support posts 43 extend over and between theactuator body 30 upper surface and connectingplate 48 lower surface with the positions thereof restricted. In this state, of thesupport post portions support post portions actuator body 30. And, support holes 51 b, 51 b, which are formed in the lower-side support plate 25 b of the above-mentioned pair ofsupport plates support post portions support posts support post portions plate 48. And, in the upper-side support plate 25 a of the pair ofsupport plates support post portions support posts - By the way, in the illustrated embodiment, in the lower-
side support plate 25 b, there are disposed projectingportions trunnions portions support plate 25 b. These three projectingportions trunnions pivot shafts trunnions portions peripheral surfaces power rollers trunnions input side disks output side disk 16 c from the input and output side surfaces 3, 17 of thesedisks - Also, of the
actuator body 30 and connectingplate 48 which are connected to each other by the pair of support posts 43, 43, theactuator body 30 is fixed to the lower portion of thecasing 11. To realize this fixation, in the near-to-opening portion of the lower end of the inner surface of thecasing 11, there aredisposed stage portions actuator body 30 in the width direction thereof (in FIGS. 1 and 2, in the front and back direction; and, in FIG. 3, in the right and left direction), there are formed bolt insertion holes 54, 54 (FIG. 4)). When fixing theactuator body 30 to the interior of thecasing 11, the near-to-width-direction-two-end portions of the upper surface of theactuator body 30 are butted against thestage portions respective stage portions - On the other hand, the connecting
plate 48 is mounted in the interior of thecasing 11 in such a manner that the positions thereof in the length direction (in FIGS. 1 and, in the right and left direction; and, in FIG. 3, in the front and back direction) and in the width direction thereof are restricted. To enforce this position restriction, in the mutually opposing portions of the upper surface of the connectingplate 48 and the lower surface of thetop plate portion 55 of thecasing 11, there are formed positioning recessedportions portion actuator body 30 is fixed to the interior of thecasing 11, there are set cylindrical-shapedpositioning sleeves portions plate 48 and the positioning recessedportions top plate portion 55. Due to this structure, the respective upper and lower end portions of the pair of support posts 43, 43 are supported on and fixed to thecasing 11 in such a manner that they are positioned. - The
output side disk 16 c is rotatably supported by thesupport ring portions casing 11 in the above-mentioned manner but also are respectively present in the central portions of the cavities (spaces) existing between the respective side surfaces of theinput side disks output side disk 16 c. To realize this, the respective thrustangular ball bearings support ring portions output side disk 16 c, that is, an inside diameter side portion more interior than the output side surfaces 17, 17 that are disposed on the axial-direction two side surfaces of theoutput side disk 16 c In the case of the illustrated embodiment, on the near-to-inside-diameter portions of the outer surfaces (the mutually opposite-side side surfaces) of a pair ofraces angular ball bearings strip portions 59, 59 (FIG. 2A) over the entire peripheries of the present near-to-inside-diameter portions. - And, the projecting-
strip portions support ring portions output side disk 16 c with no play between them, thereby setting the positions of the thrustangular ball bearings shim plates 60, 60 (FIG. 2A) are interposed respectively between the outer surfaces of theraces support ring portions angular ball bearings angular ball bearings output side disk 16 c is rotatably supported between the support posts 43, 43, which are disposed one pair in each of the cavities, in such a manner that it is positioned not only in the diameter direction thereof but also in the axial direction thereof. - Also, in the case of the illustrated continuously variable transmission apparatus, the base end portion (in FIG. 1, the left end portion) of the input
rotary shaft 1 a is connected through adrive shaft 61 to a crankshaft (not shown) of an engine (not shown), so that the inputrotary shaft 1 a can be driven and rotated by the crankshaft. Also, as apressing device 6a which is used to apply proper surface pressures to the rolling contact portions (traction portions) of the axial-direction one-side surfaces of the twoinput side disks output side disk 16 c with respect to the peripheral surfaces of thepower rollers pressing device 6 a andactuators trunnions low speed clutch 62 and a high speed clutch 63 (both of which will be discussed later). - Also, the base end portion (in FIGS. 1 and 2, the left end portion) of a
hollow rotary shaft 64 is spline engaged with theoutput side disk 16 c. And, thehollow rotary shaft 64 is inserted into the distant-from-engine side (in FIGS. 1 and 2, the right side) of the inner side of theinput side disk 2 b, so that the rotation power of theoutput side disk 16 c can be taken out. Further, to the portion of the leading end portion (in FIGS. 1 and 2, the right end portion) of thehollow rotary shaft 64 that projects from the outer surface of theinput side disk 2 b, there is fixed afirst sun gear 65 which is used to constitute the first planetary-gear-type transmission unit 34. - On the other hand, between the
input side disk 2 b and the portion of the leading end portion (in FIGS. 1 and 2, the right end portion) of the inputrotary shaft 1 a that projects from thehollow rotary shaft 64, there is interposed afirst carrier 66 so as to extend between and over them, so that theinput side disk 2 b and inputrotary shaft 1 a can be rotated in synchronization with each other. And, at several circumferential-direction equidistant positions (generally, at three or four positions) of the axial-direction two side surfaces of thefirst carrier 66, there are rotatably supportedplanetary gears 67˜69 which are used to constitute the first and second planetary-gear-type transmission units first carrier 66, there is rotatably supported afirst ring gear 70. - Of the
planetary gears 67˜69, theplanetary gear 67, which is situated near to the toroidal-type continuously variable transmission unit 33 (in FIGS. 1 and 2, situated near to the left side) and is disposed inside with respect to the diameter direction of thefirst carrier 66, is meshingly engaged with thefirst sun gear 65. Also, theplanetary gear 68, which is situated on the distant side (in FIGS. 1 and 2, on the right side) from the toroidal-type continuouslyvariable transmission unit 33 and is disposed inside with respect to the diameter direction of thefirst carrier 66, is meshingly engaged with asecond sun gear 71 which is fixed to the base end portion (in FIG. 1, the left end portion) of thetransmission shaft 38. Further, the remainingplanetary gears 69, which are respectively disposed outside with respect to the diameter direction of thefirst carrier 66, are set larger in the axial-direction dimension than the twoplanetary gears planetary gears 69 are meshingly engaged with the twoplanetary gears planetary gears 69 are meshingly engaged with thefirst ring gear 70. By the way, it is also possible to employ a structure that, instead of the two outside disposed (with respect to the diameter direction of the carrier 66) planetary gears being used independently of each other, a wide ring gear is meshingly engaged with these two planetary gears. - On the other hand, a
second carrier 72 for constituting the third planetary-gear-type transmission unit 36 is connected and fixed to the base end portion (in FIG. 1, the left end portion) of theoutput shaft 37. And, thesecond carrier 72 is connected to thefirst ring gear 70 through thelow speed clutch 62. Also, athird sun gear 73 is fixedly secured to the near-to-front-end portion (in FIGS. 1 and 2, the near-to-right-end portion) of thetransmission shaft 38. Further, on the periphery of thethird sun gear 73, there is disposed asecond ring gear 74; and, thehigh speed clutch 63 is interposed between thesecond ring gear 74 and a fixed portion such as thecasing 11. In addition, two or more sets ofplanetary gears second ring gear 74 andthird sun gear 73, are rotatably supported on thesecond carrier 72. Theseplanetary gears planetary gears 75, which are disposed inside with respect to the diameter direction of thesecond carrier 72, are meshingly engaged with thethird sun gear 73, while theplanetary gears 76 disposed outside with respect to the diameter direction of thesecond carrier 72 are meshingly engaged with thesecond ring gear 74. - In the case of the above-structured continuously variable transmission apparatus according to the present embodiment, the power, which has been transmitted from the input
rotary shaft 1 a through the pair ofinput side disks respective power rollers output side disk 16 c, is taken out through thehollow rotary shaft 64. In a state where thelow speed clutch 62 is connected and the connection of thehigh speed clutch 63 is cut off, in case where the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33 is changed, while maintaining constant the rotation speed of the inputrotary shaft 1 a, the rotation speed of theoutput shaft 37 can be switched from a forward rotation condition to a reverse rotation condition or vice versa with a stopping condition between them. That is, in this state, a differential component between thefirst carrier 66 rotating in the forward direction together with the inputrotary shaft 1 a and thefirst sun gear 65 rotating in the opposite direction together with thehollow rotary shaft 64 is transmitted from thefirst ring gear 70 through thelow speed clutch 62 andsecond carrier 72 to theoutput shaft 37. In this state, by setting the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33 at a given value, theoutput shaft 37 can be stopped; and, besides, by changing the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33 from the above-mentioned given value to the speed increasing side, theoutput shaft 37 can be rotated in the direction to back the vehicle. On the other hand, in case where the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33 is changed from the above given value to the speed reducing side, theoutput shaft 37 can be rotated in the direction to advance the vehicle. - Further, in a state where the connection of the
low speed clutch 62 is cut off and thehigh speed clutch 63 is connected, theoutput shaft 37 is rotated in the direction to advance the vehicle. That is, in this state, the rotation power of theplanetary gear 67 of the first planetary-gear-type transmission unit 34 rotatable in accordance with the differential component between thefirst carrier 66 rotating in the forward direction together with the inputrotary shaft 1 a and thefirst sun gear 65 rotating in the opposite direction together with thehollow rotary shaft 64 is transmitted through theplanetary gear 69 to theplanetary gear 68 of the second planetary-gear-type transmission unit 35, thereby rotating thetransmission shaft 38 through thesecond sun gear 71. And, due to the mutually meshingly engagement between thethird sun gear 73 disposed on the leading end portion of thetransmission shaft 38 and thesecond ring gear 74 andplanetary gears third sun gear 73 in constituting the third planetary-gear-type transmission unit 36, thesecond carrier 72 and theoutput shaft 37 connected to thesecond carrier 72 are rotated in the direction to advance the vehicle. In this state, more shift the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33 into the speed increasing side, the more be fast the rotation speed of theoutput shaft 37. - Now, FIG. 6 shows an example of the relationship between the transmission ratio (the speed reduction ratio) of the toroidal-type continuously
variable transmission unit 33 and the speed ratio of the whole of the continuously variable transmission apparatus. The vertical axis of FIG. 6 represents the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33, while the horizontal axis of FIG. 6 stands for theoretical vehicle speeds (km/h) when the inputrotary shaft 1 a is rotated at a constant speed (5600 min −1) by an engine of about 3L displacement. As can be seen clearly from FIG. 6, by setting the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33 at a value of about 0.6 in a state where thelow speed clutch 62 is connected and thehigh speed clutch 63 is disconnected, while leaving the inputrotary shaft 1 a in rotation, theoutput shaft 37 can be stopped. Also, by changing the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33 with the value of about 0.6 as the boundary value, the vehicle can be advanced or backed. Further, in case where the boundary value of the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33 is in the range of about 2.2˜2.3, by changing the transmission ratio of the toroidal-type continuouslyvariable transmission unit 33 to the speed increasing side in a state where thelow speed clutch 62 is disconnected and thehigh speed clutch 63 is connected, the speed of the vehicle can be increased. - To assemble the continuously variable transmission apparatus structured and operatable in the above-mentioned manner, the toroidal-type continuously
variable transmission unit 33 as well as the first and second planetary-gear-type transmission units casing 11 before they are stored into thecasing 11. That is, using the pair of support posts 43, 43 (see FIGS. 1˜3) having their respective lower ends connected and fixed to theactuator body 30, theoutput side disk 16 c and hollowrotary shaft 64 can be rotatably supported. Also, using the pair of upper andlower support plates support post portions support posts trunnions power rollers pressing device 6 a, the pair ofinput side disks type transmission unit rotary shaft 1 a which is inserted through thehollow rotary shaft 64. - Therefore, the main portions of the toroidal-type continuously
variable transmission unit 33 as well as the first and second planetary-gear-type transmission units casing 11 before they are stored into thecasing 11, thereby being able to produce amodule 77 which is shown in FIG. 4 and provides the main portions of the continuously variable transmission apparatus. The assembling operation of themodule 77 can be executed in a wide space with no interference with thecasing 11; that is, the assembling operation can be facilitated. Also, after assembly of themodule 77, before themodule 11 is stored into thecasing 11, the operation condition of themodule 77 can be confirmed. And, in case where the operation condition of themodule 77 is found poor, themodule 77 can be taken into original composing parts and the-thus-dismantled parts can be assembled again easily in a wide space outside thecasing 11. - On the other hand, in case where the operation condition of the-
module 77 is found proper, themodule 77 is inserted into thecasing 11 from the lower end opening of thecasing 11 with the connectingplate 48 facing upwardly. And, the cylindrical-shapedpositioning sleeves portions plate 48 and the positioning recessedportions top plate portion 55, near-to-two-end portions of the upper surface of theactuator body 30 are respectively butted against thestage portions actuator body 30 from bottom are threadedly engaged with the screw holes formed in thestage portions module 77 to the interior of thecasing 11 After completion of the fixing operation, the lower end opening of thecasing 11 is closed by anoil pan 81. - By the way, the composing parts not included in the
module 77 such as the third planetary-gear-type transmission unit 36 are assembled to the interior of thecasing 11 after themodule 77 is assembled to the interior of thecasing 11. Also, in the illustrated embodiment, on the upper portions of the support posts 43, 43, there are disposedoil supply nozzles oil supply nozzles top plate portion 55 and connectingplate 48 through the positioning recessedportions bolts trunnions oil supply passages power rollers top plate portion 55 into theoil supply passages trunnions plate 48, there are disposed oil supply plugs 79, 79 which are used to feed the lubricating oil to theoil supply passages module 77 is stored into thecasing 11, the oil supply passage on the connectingplate 48 side and the oil supply passages on thetrunnions output side disk 16 c and in the outer peripheral edge of the pressing device, there are formed the diameter-direction uneven portions at regular intervals in the circumferential direction thereof, thereby being able to detect the rotation speeds of theoutput side disk 16 c andinput side disks - In the case of the toroidal-type continuously
variable transmission unit 33 constituting themodule 77 which is stored into thecasing 11 in the above-mentioned manner, differently from the conventional structure shown in the previously-described FIG. 7, there is eliminated the need to interpose the rollingbearings bearings output side disks output side disk 16 c, which makes it possible to reduce the axial-direction dimension of the installation portion of theoutput side disk 16 c. Thus, the toroidal-type continuouslyvariable transmission unit 33 can be reduced in size and weight by an amount corresponding to the reduction in the axial-direction dimension. - Further, according to the present embodiment, since the
output side disk 16 c is formed as an integral structure in which the axial-direction two side surfaces thereof are used as the output side surfaces 17, 17, the forces to be applied to the output side surfaces 17, 17 when the toroidal-type continuouslyvariable transmission unit 33 is in operation can be mutually cancelled within theoutput side disk 16 c. As a result of this, theoutput side disk 16 c can be restricted in the elastic deformation regardless of the moment loads that are applied from thepower rollers output side disk 16 c and, therefore, the toroidal-type continuously variable transmission can be reduced in size and weight in this respect as well. - By the way, the output gear may also be integrally disposed on the outer peripheral edge of the integrally-formed output side disk. In case where such structure is employed, a transmission shaft for taking out the power from the output side disk may be disposed in parallel to the input rotary shaft. And, another gear fixedly disposed on the end portion of the transmission shaft may be meshingly engaged with the output gear.
- Since the invention is structured and operates in the above-mentioned manner, the assembling operation thereof can be facilitated and, therefore, not only the cost of a toroidal-type continuously variable transmission can be reduced but also the repairing operation thereof can be facilitated.
- Also, because the axial-direction dimension of the toroidal-type continuously variable transmission can be reduced, while securing the necessary performance thereof, the size and weight thereof can be reduced, which makes it possible for the present toroidal-type continuously variable transmission to be assembled to a vehicle body of a smaller size. That is, the invention can contribute toward practical use of the toroidal-type continuously variable transmission.
Claims (15)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2002243389A JP4123869B2 (en) | 2002-08-23 | 2002-08-23 | Toroidal continuously variable transmission and continuously variable transmission |
JPP.2002-243389 | 2002-08-23 |
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US20040058772A1 true US20040058772A1 (en) | 2004-03-25 |
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US10/644,770 Expired - Lifetime US6872162B2 (en) | 2002-08-23 | 2003-08-21 | Toroidal-type continuously variable transmission and continuously variable transmission apparatus |
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US (1) | US6872162B2 (en) |
JP (1) | JP4123869B2 (en) |
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US6872162B2 (en) | 2005-03-29 |
JP4123869B2 (en) | 2008-07-23 |
JP2004084712A (en) | 2004-03-18 |
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